CN212318268U - Pumping machine and pumping system thereof - Google Patents

Abstract

The embodiment of the application provides a pumping machine and pumping system thereof, including assisting pipe, the conveying pipe that the cylinder and be used for carrying the concrete of preventing cutting off of propelling movement piston, at pumping system switching-over in-process, the piston rod drive propelling movement piston through the cylinder that prevents cutting off moves towards the by-pass mouth in order to supply the concrete in the inner chamber to the material chamber. Therefore, the concrete in the inner cavity is supplemented to the material cavity by driving the pushing piston, so that the continuous pumping of the concrete at the discharge port of the conveying pipe is basically realized, and the concrete disconnection at the discharge port of the conveying pipe is avoided.

Description

Pumping machine and pumping system thereof

Technical Field

The application relates to the technical field of concrete pumping, in particular to pumping machinery and a pumping system thereof.

Background

The existing pumping machinery such as a pump truck and a vehicle-mounted pump for concrete is basically a piston type concrete pump, and the working principle of the pumping machinery is that two main oil cylinders are driven by a pumping loop to alternately act to push working pistons in concrete cylinders to convey concrete in a linear reciprocating manner, and meanwhile, a distribution loop drives two swing valve oil cylinders to drive an S pipe to be in response fit with the S pipe, so that the concrete is conveyed to a construction point from a discharge port. In the actual working process, the discharge port of the conveying pipe is difficult to continuously output concrete, and the phenomenon of concrete high-pressure column cutoff occurs.

SUMMERY OF THE UTILITY MODEL

In view of the above, embodiments of the present application are intended to provide a pumping machine and a pumping system thereof, so as to substantially realize continuous concrete output from a discharge port of a delivery pipe.

To achieve the above object, a first aspect of embodiments of the present application provides a pumping system, including:

the conveying pipe is used for conveying concrete, a material cavity, a feeding hole, a discharging hole and a bypass port are formed, the feeding hole, the discharging hole and the bypass port are all communicated with the material cavity, and the bypass port is located between the feeding hole and the discharging hole;

the end part of the auxiliary pipe is covered around the bypass port, an inner cavity is formed in the auxiliary pipe, and the inner cavity is communicated with the material cavity through the bypass port;

the pushing piston is arranged in the inner cavity in a sealing and sliding mode; and

the anti-blocking oil cylinder is arranged on one side, away from the bypass port, of the pushing piston, and a piston rod of the anti-blocking oil cylinder is connected with the pushing piston;

in the reversing process of the pumping system, a piston rod of the anti-blocking oil cylinder drives the pushing piston to move towards the bypass port so as to supplement concrete in the inner cavity into the material cavity.

In one embodiment, the pumping system further comprises a first oil inlet passage, a first working oil passage and a cutoff-preventing valve group, wherein a first end of the first working oil passage is communicated with the cutoff-preventing oil cylinder, and the cutoff-preventing valve group selectively communicates the first oil inlet passage with the first working oil passage or returns the first working oil passage;

in the reversing process of the pumping system, the anti-blocking valve group is communicated with the first oil inlet oil way and the first working oil way so as to enable a piston rod of the anti-blocking oil cylinder to extend out; during the pumping process of the pumping system, the anti-blocking valve group returns oil to the first working oil path so as to retract a piston rod of the anti-blocking oil cylinder.

In one embodiment, the anti-blocking valve group comprises a first pilot valve, a hydraulic control reversing valve, a first pilot oil path, a second pilot oil path and a third pilot oil path, and the pumping system further comprises a fourth pilot oil path;

the hydraulic control reversing valve comprises a second oil inlet, a second oil return port, a third working oil port, a second control oil port and a third control oil port;

the first pilot valve comprises a first oil inlet, a first oil return port, a first working oil port, a second working oil port and a first control oil port, the second end of the first working oil way is communicated with the third working oil port, the first end of the first pilot oil way is communicated with the first oil inlet oil way, the second end of the first pilot oil way is communicated with the first oil inlet, the first end of the second pilot oil way is communicated with the first working oil port, the first end of the third pilot oil way is communicated with the second working oil port, and the first end of the fourth pilot oil way is communicated with the first control oil port;

the first pilot valve comprises a first working position and a second working position, when the first pilot valve is located at the first working position, the first oil inlet is communicated with the first working oil port, and the second working oil port is communicated with the first oil return port; when the first pilot valve is located at a second working position, the first oil inlet is communicated with the second working oil port, and the first working oil port is communicated with the first oil return port;

the first end of the first oil inlet oil path is communicated with the second oil inlet, the second end of the second pilot oil path is communicated with the second control oil port, and the second end of the third pilot oil path is communicated with the third control oil port;

the hydraulic control reversing valve comprises a third working position and a fourth working position, when the hydraulic control reversing valve is located at the third working position, the second oil inlet is stopped, and the third working oil port is communicated with the second oil return port; when the hydraulic control reversing valve is located at a fourth working position, the second oil inlet is communicated with the third working oil port, and the second oil return port is closed;

in the reversing process of the pumping system, the first pilot valve is in the second working position, and the hydraulic control reversing valve is in the fourth working position; in the pumping process of the pumping system, the first pilot valve is in a first working position, and the hydraulic control reversing valve is in a third working position.

In one embodiment, the pumping system further comprises a first throttle valve disposed on the fourth pilot oil passage.

In one embodiment, the pumping system further includes a first pressure relief oil path and a second throttle valve disposed on the first pressure relief oil path, and one end of the first pressure relief oil path is communicated with a fourth pilot oil path on a side of the first throttle valve away from the first control oil port.

In one embodiment, the pumping system further comprises:

two main oil cylinders for alternately pumping concrete;

each main oil cylinder is correspondingly provided with one signal oil way, the first end of each signal oil way is communicated with the corresponding main oil cylinder, and the second ends of the two signal oil ways are alternatively used for supplying oil to the fourth pilot oil way; and

each signal oil way is provided with one signal valve group, and the signal valve groups selectively conduct the corresponding signal oil ways;

in the reversing process of the pumping system, one of the two signal valve groups conducts the corresponding signal oil way; in the pumping process of the pumping system, each signal valve group cuts off the corresponding signal oil path.

In one embodiment, the pumping system includes a first shuttle valve, a second end of one of the two signal oil paths is communicated with one of the oil inlets of the first shuttle valve, a second end of the other of the two signal oil paths is communicated with the other of the oil inlets of the first shuttle valve, and an oil outlet of the first shuttle valve is communicated with a second end of the fourth pilot oil path.

In an embodiment, each master cylinder is provided with a first collecting oil port and a second collecting oil port, the first collecting oil port and the second collecting oil port are arranged at intervals along the axial direction of the corresponding master cylinder, the first collecting oil port is located on one side of the second collecting oil port, which extends towards the piston rod of the master cylinder, and a first end of the signal oil path is communicated with the first collecting oil port of the corresponding master cylinder;

the signal valve group includes:

the cartridge valve is arranged on the signal oil path;

a first end of the first control oil way is communicated with a control oil port of the cartridge valve, and a second end of the first control oil way is communicated with a second collecting oil port of the corresponding main oil cylinder;

a first end of the connecting oil way is communicated with the first control oil way, and a signal oil way between the oil inlet of the cartridge valve and the corresponding first collecting oil port is communicated with a second end of the connecting oil way; and

the third throttle valve is arranged on the connecting oil path;

in the reversing process of the pumping system, a piston of one of the two main oil cylinders is positioned between the corresponding first collecting oil port and the second collecting oil port and moves along the direction departing from the corresponding first collecting oil port, and the corresponding cartridge valve is opened to conduct the corresponding signal oil way; in the pumping process of the pumping system, a first collecting oil port and a second collecting oil port of one of the two master oil cylinders are located on one side of the corresponding piston, or a piston of one of the two master oil cylinders is located between the corresponding first collecting oil port and the corresponding second collecting oil port and moves towards the direction of the corresponding first collecting port, a first collecting oil port and a second collecting oil port of the other of the two master oil cylinders are located on one side of the corresponding piston, or a piston of the other of the two master oil cylinders is located between the corresponding first collecting oil port and the corresponding second collecting oil port and moves towards the direction of the corresponding first collecting port, and each cartridge valve is closed to stop the corresponding signal oil path.

In one embodiment, the signal valve group further includes a check valve, the check valve is disposed on a signal oil path between an oil inlet of the cartridge valve and the corresponding first collecting oil port, the cartridge valve is disposed on the signal oil path on one side of an oil outlet of the check valve, and the signal oil path between the oil inlet of the cartridge valve and the oil outlet of the check valve is communicated with the second end of the connecting oil path.

In an embodiment, the signal valve group further includes a fourth throttle valve and a fifth throttle valve, and the fourth throttle valve and the fifth throttle valve are disposed on the signal oil path between the oil inlet of the check valve and the corresponding first collecting oil port.

In an embodiment, the pumping system further includes a second pressure relief oil path and a sixth throttle valve disposed on the second pressure relief oil path, each signal oil path is correspondingly provided with the second pressure relief oil path, and the second pressure relief oil path is communicated with the signal oil path on one side of the oil outlet of the corresponding cartridge valve.

In one embodiment, the pumping system further comprises:

the second end of the first oil inlet channel is communicated with an oil outlet of the second shuttle valve;

a first end of the second oil inlet path is communicated with one oil inlet of the second shuttle valve;

a first end of the second oil inlet path is communicated with one oil inlet of the second shuttle valve; and

the second end of the second oil inlet channel is communicated with one rodless cavity of the tilt cylinder, and the second end of the third oil inlet channel is communicated with the other rodless cavity of the tilt cylinder;

during the reversing process of the pumping system, the tilt cylinder is reversed, and one of the two rodless cavities of the tilt cylinder is communicated with the anti-flow-cutoff oil cylinder, so that a piston rod of the anti-flow-cutoff oil cylinder extends out.

A second aspect of embodiments of the present application provides a pumping machine comprising a pumping system of any of the above.

According to the pumping system, in the reversing process of the pumping system, the piston rod of the cutoff-preventing oil cylinder drives the pushing piston to move towards the bypass port so as to supplement concrete in the inner cavity to the material cavity. Therefore, the concrete in the inner cavity is supplemented to the material cavity by driving the pushing piston, so that the continuous pumping of the concrete at the discharge port of the conveying pipe is basically realized, and the concrete disconnection at the discharge port of the conveying pipe is avoided.

Drawings

FIG. 1 is a schematic diagram of a prior art pumping system;

FIG. 2 is a schematic diagram of a pumping system according to an embodiment of the present application;

FIG. 3 is a hydraulic schematic diagram of the actuation of the anti-drainback cylinder according to an embodiment of the present application;

FIG. 4 is a hydraulic schematic diagram of an anti-shut-off valve set and an external oil path thereof according to an embodiment of the present disclosure;

fig. 5 is a hydraulic schematic diagram of a signal valve set and a corresponding master cylinder according to an embodiment of the present application.

Description of reference numerals:

a delivery pipe 1; a material chamber 11; a feed inlet 12; a discharge port 13; a bypass port 14;

an auxiliary pipe 2; an inner cavity 21;

a push piston 3; a cutoff prevention oil cylinder 4;

a first oil inlet passage 500; a first working oil path 501; fourth pilot oil passage 502; a first throttle valve 503; a first relief oil passage 504; a second throttle valve 505; a signal oil path 506; a first shuttle valve 507; a second relief oil passage 508; a sixth throttle valve 509; a second shuttle valve 510; the second oil inlet passage 511; a third oil inlet passage 512; a tilt cylinder 513; a second working oil passage 514; the third working oil passage 515;

an anti-shut off valve block 6;

a first pilot valve 61; a first oil inlet 611; a first oil return port 612; a first working port 613; a second working oil port 614; a first control port 615;

a pilot operated directional control valve 62; a second oil inlet 621; a second oil return path 622; a third working oil port 623 and a fourth working oil port 624; a second control port 625; a third control oil port 626;

first pilot oil passage 63; second pilot oil passage 64; a third pilot oil passage 65;

a master cylinder 7; a first oil collection port 71; a second oil collection port 72;

a signal valve group 8; a cartridge valve 81; the first control oil passage 82; a connection oil passage 83; a third throttle valve 84; a check valve 85; a fourth throttle valve 86; a fifth throttle valve 87;

a main valve group 9;

first oil supply passage P1; a first oil return passage T1; second oil supply passage P2; a second oil return path T2;

a concrete cylinder 100; an S tube 200; a hopper 300.

Detailed Description

It should be noted that, in the present application, technical features in examples and embodiments may be combined with each other without conflict, and the detailed description in the specific embodiment should be understood as an explanation of the gist of the present application and should not be construed as an improper limitation to the present application.

The embodiment of the application provides a pumping machine, and the pumping machine can be any one of a pump truck, a vehicle-mounted pump and a trailer pump. The embodiment of the present application takes a pumping machine as an example for explanation.

The pumping machine such as a pump truck or a vehicle-mounted pump comprises a chassis, a pumping system arranged on the chassis and an arm support, wherein the arm support of the pump truck or the vehicle-mounted pump can be a folding arm support. For pumping machinery such as a towing pump, a chassis is not provided, and the arm support of the supporting pump is a fixed arm support which is fixedly arranged on a building. And are not intended to be limiting herein.

Before describing the embodiments of the present application, it is necessary to analyze the reason for the concrete flow interruption at the discharge port 13 of the delivery pipe 1 of the pumping system of the prior art, and reasonably analyze the technical solution of the embodiments of the present application.

Through analysis, referring to fig. 1, the pumping system in the prior art includes two master cylinders 7, two concrete cylinders 100, a tilt cylinder 513, a swing arm, an S-pipe 200, and a hopper 300, wherein each master cylinder 7 is correspondingly provided with one concrete cylinder 100, and each concrete cylinder 100 is selectively communicated with a containing cavity of the hopper 300. One end of the S-pipe 200 is rotatably connected to the hopper 300, the S-pipe 200 is connected to the swing arm, and the swing arm drives the S-pipe 200 to rotate under the driving of the swing cylinder 513 so that the other end of the S-pipe is alternatively communicated with the two concrete cylinders 100. When the S pipe 200 is communicated with one of the two concrete cylinders 100, the other concrete cylinder 100 is communicated with the hopper 300, the concrete cylinder 100 communicated with the S pipe 200 is driven by the corresponding main oil cylinder 7 to pump concrete to the S pipe 200, the concrete cylinder 100 communicated with the hopper 300 is driven by the corresponding main oil cylinder 7 to suck the concrete from the hopper 300, so that the concrete is communicated with the S pipe 200 after the direction is changed, and the concrete sucked from the hopper 300 is pumped to the S pipe 200. After the direction is changed, the concrete cylinder originally communicated with the S pipe 200 is changed to be communicated with the hopper 300, and the material is sucked from the hopper 300. The concrete is alternately pumped in this way. The piston rod of each master cylinder 7 is connected with the piston of the corresponding concrete cylinder 100, and the piston rod of the master cylinder 7 pushes the piston of the concrete cylinder 100 to move, so that the concrete cylinder 100 can suck or pump concrete. The piston of the master cylinder 7 and the piston of the concrete cylinder 100 move synchronously. In the concrete conveying process, the optimal state is that the switching time of the working oil cylinder of the pumping loop when the working oil cylinder is reversed to the head is extremely short, preferably short enough not to influence the continuous pushing of the concrete, and simultaneously, the time sequence logic relation of the distribution loop matched with the switching time sequence logic relation is also in seamless butt joint and is synchronous to have no time difference, so that hydraulic impact in any form can not be generated. But the actual situation is: when the working piston or the S-tube 200 in the concrete cylinder 100 is reversed, that is, the pumping system is in a reversed state, the switching time is inevitable in both the pumping loop and the distribution loop, and the timing logic relationship between the two has the problem of leading or lagging. Although both the two times are very short, the reversing process can slow down the moving speed of the piston of the main oil cylinder 7 and the piston of the concrete cylinder 100, inevitably affects the pushing of the conveyed concrete high-pressure column, and even in the short time, the concrete high-pressure column loses the pushing force, thereby causing the phenomenon of 'cutoff' of the concrete high-pressure column.

The phenomenon of flow interruption causes the regular and intermittent delivery of the concrete delivery flow in the delivery pipe 1, which will generate periodic vibration to the pump truck body and the arm support. When the arm support is unfolded and pumping construction is carried out, the arm support is dozens of meters long, and any micro vibration of the machine body can enable the arm support to swing to a large extent. The vibration of the machine body and the arm support also deteriorates the stability of the pump truck, which may cause the entire truck to tip over.

In view of this, the present embodiment provides a pumping system, referring to fig. 2 to 5, including a delivery pipe 1, an auxiliary pipe 2, a pushing piston 3 and a cutoff-preventing cylinder 4. The conveying pipe 1 is used for conveying concrete, a material cavity 11, a feeding hole 12, a discharging hole 13 and a bypass port 14 are formed in the conveying pipe 1, the feeding hole 12, the discharging hole 13 and the bypass port 14 are all communicated with the material cavity 11, and the bypass port 14 is located between the feeding hole 12 and the discharging hole 13. The end part of the auxiliary pipe 2 is covered around the bypass port 14, the auxiliary pipe 2 is provided with an inner cavity 21, and the inner cavity 21 is communicated with the material cavity 11 through the bypass port 14. The thrust piston 3 is arranged in a sealing sliding manner in the interior 21. The anti-cutoff oil cylinder 4 is arranged on one side, away from the bypass port 14, of the pushing piston 3, and a piston rod of the anti-cutoff oil cylinder 4 is connected with the pushing piston 3.

In the embodiment of the application, the reversing process of the pumping system refers to the process from the moment when the pumping system sends a reversing signal to the moment when the piston of the main oil cylinder starts to move reversely. The pumping system realizes the alternate pumping of materials through a reversing process. How to realize the alternate pumping of the materials is a conventional technical means in the field, and the description is not repeated. The reversing signal is not hydraulic oil in the signal oil path but an electric signal, the reversing signal can be triggered by a differential pressure switch, and the specific way of triggering the electric signal by the differential pressure switch is a conventional technical means in the field, and is not described in detail herein.

During the reversing process of the pumping system, the piston rod of the anti-blocking oil cylinder 4 drives the pushing piston 3 to move towards the bypass opening 14 so as to supplement the concrete in the inner cavity 21 to the material cavity 11. Therefore, the concrete in the inner cavity 21 is supplemented to the material cavity 11 by driving the pushing piston 3, so that the concrete at the discharge port 13 of the conveying pipe 1 basically realizes continuous pumping, and the concrete at the discharge port 13 of the conveying pipe 1 is prevented from being broken.

The pumping system of the embodiment of the application basically realizes the continuous pumping of the concrete at the discharge port 13 of the delivery pipe 1, relieves the phenomenon that the regular and intermittent delivery of the concrete delivery flow in the delivery pipe 1 causes the vibration of the body and the arm support of the pumping machine (such as a pump truck), and is favorable for improving the stability of the pumping machine.

The pumping system of the embodiment of the application can even nearly eliminate the phenomenon that the regular and intermittent delivery of the concrete delivery flow in the delivery pipe 1 causes vibration to the body and the arm support of the pumping machine (such as a pump truck).

In one embodiment, the cylinder body of the anti-flow-break cylinder 4 is connected with the auxiliary pipe 2 so as to install and fix the anti-flow-break cylinder 4.

In an embodiment, referring to fig. 3 and 4, the pumping system further includes a first oil inlet path 500, a first working oil path 501, and a cut-off prevention valve set 6, wherein a first end of the first working oil path 501 is communicated with the cut-off prevention cylinder 4, and the cut-off prevention valve set 6 selectively communicates the first oil inlet path 500 with the first working oil path 501, or returns the first working oil path 501. In the reversing process of the pumping system, the anti-breaking valve group 6 is communicated with the first oil inlet oil way 500 and the first working oil way 501 so as to extend a piston rod of the anti-breaking oil cylinder 4; during pumping of the pumping system, the anti-shut-off valve group 6 returns the first working oil path 501 to retract the piston rod of the anti-shut-off cylinder 4.

In the embodiment of the application, the pumping process of the pumping system refers to a process from the time when the main oil cylinder starts to push concrete to the time when the main oil cylinder sends a reversing signal.

It will be appreciated that extension of the piston rod of the anti-shut off cylinder 4 will drive the push piston 3 towards the bypass port 14 to replenish the concrete in the inner chamber 21 into the material chamber 11, so that the concrete in the feed pipe 1 can be substantially continuously pumped from the discharge outlet 13 of the feed pipe 1 to a target location, for example a point of application where pumping is required. It can be understood that, in the pumping process of the pumping system, since the anti-blocking valve group 6 returns the oil to the first working oil path 501, the anti-blocking oil cylinder 4 communicated with the first end of the first working oil path 501 is in a pressure relief state, and the concrete in the conveying pipe 1 is in a normal pumping pressure state, the pressure of the pumped concrete is relatively high, and part of the concrete in the conveying pipe 1 enters the inner cavity 21 of the auxiliary pipe 2 through the bypass port 14 to apply an acting force to the pushing piston 3, so that the piston rod of the anti-blocking oil cylinder 4 connected with the pushing piston 3 retracts. The concrete entering the inner cavity 21 of the auxiliary pipe 2 is prepared for supplementing the concrete to the conveying pipe 1 in the reversing process of the pumping system.

It will be appreciated that the anti-shut off cylinder 4 may be a piston cylinder or a plunger cylinder. When the anti-breaking oil cylinder 4 is a piston cylinder, the piston rod refers to a piston rod connected to the piston of the anti-breaking oil cylinder 4, and the first end of the first working oil path 501 is communicated with the rodless cavity of the anti-breaking oil cylinder 4. When the anti-flow-cutoff oil cylinder 4 is a plunger cylinder, the piston rod is a plunger, the plunger cylinder has only one oil cavity, and the first end of the first working oil path 501 is communicated with the oil cavity of the plunger cylinder. The embodiment of the application takes the cutoff oil cylinder 4 as a piston cylinder as an example for explanation.

In an embodiment, referring to fig. 3 and 4, the anti-breaking valve set 6 includes a first pilot valve 61, a pilot-controlled directional valve 62, a first pilot oil path 63, a second pilot oil path 64, and a third pilot oil path 65. The pumping system further comprises a fourth pilot oil circuit 502. The first pilot valve 61 includes a first oil inlet 611, a first oil return port 612, a first working oil port 613, a second working oil port 614 and a first control oil port 615, the second end of the first working oil path 501 is communicated with the third working oil port 623, the first end of the first pilot oil path 63 is communicated with the first oil inlet path 500, the second end of the first pilot oil path 63 is communicated with the first oil inlet 611, the first end of the second pilot oil path 64 is communicated with the first working oil port 613, the first end of the third pilot oil path 65 is communicated with the second working oil port 614, and the first end of the fourth pilot oil path 502 is communicated with the first control oil port 615. The first pilot valve 61 comprises a first working position and a second working position, when the first pilot valve 61 is in the first working position, the first oil inlet 611 is communicated with the first working oil port 613, and the second working oil port 614 is communicated with the first oil return port 612; when the first pilot valve 61 is in the second working position, the first oil inlet 611 is communicated with the second working oil port 614, and the first working oil port 613 is communicated with the first oil return port 612. The hydraulic control directional control valve 62 includes a second oil inlet 621, a second oil return port, a third working oil port 623, a second control oil port 625, and a third control oil port 626, a first end of the first oil inlet path 500 is communicated with the second oil inlet 621, a second end of the second pilot oil path 64 is communicated with the second control oil port 625, and a second end of the third pilot oil path 65 is communicated with the third control oil port 626. The hydraulic control reversing valve 62 comprises a third working position and a fourth working position, when the hydraulic control reversing valve 62 is in the third working position, the second oil inlet 621 is cut off, and the third working oil port 623 is communicated with the second oil return port; when the pilot operated directional control valve 62 is in the fourth working position, the second oil inlet 621 is communicated with the third working oil port 623, and the second oil return port is closed. In the reversing process of the pumping system, the first pilot valve 61 is in the second working position, and the hydraulic control reversing valve 62 is in the fourth working position; during pumping of the pumping system, the first pilot valve 61 is in the first operating position, and the pilot-operated directional valve 62 is in the third operating position. In such a structure, in different working processes of the pumping system, corresponding oil paths are conducted by switching corresponding working positions of the pilot valve and the hydraulic control reversing valve 62, and then the piston rod of the anti-blocking oil cylinder 4 correspondingly extends or retracts.

In one embodiment, referring to fig. 3 and 4, the pilot operated directional control valve 62 further includes a fourth working port 624, and the fourth working port 624 is closed.

In one embodiment, referring to fig. 3 and 4, the pilot operated directional control valve 62 is a three-position four-way pilot operated directional control valve 62, the middle position of the pilot operated directional control valve 62 is O-shaped, and the three-position four-way pilot operated directional control valve 62 is self-reset by a spring of the three-position four-way pilot operated directional control valve 62.

In an embodiment, referring to fig. 3 and 4, the pumping system further includes a first throttle 503, and the first throttle 503 is disposed on the fourth pilot oil path 502. The first throttle 503 can weaken a pressure peak of the fourth pilot oil path 502, and avoid the pressure impact of the fourth pilot oil path 502 on the first control oil port 615, which causes frequent opening and closing of the first pilot valve 6.

In an embodiment, referring to fig. 3 and 4, the pumping system further includes a first pressure relief oil path 504 and a second throttle valve 505 disposed on the first pressure relief oil path 504, and one end of the first pressure relief oil path 504 is communicated with a fourth pilot oil path 502 on a side of the first throttle valve 503 away from the first control port 615. In such a structure, in the process that the first pilot valve 61 is reset from the second operating position to the first operating position, the hydraulic oil in the first control oil port 615 is subjected to oil return by pressure relief through the fourth pilot oil path 502 and the first pressure relief oil path 504. The second throttle valve 505 is used for enabling the fourth pilot oil path 502 to form a certain back pressure in the reversing process of the pumping system, and therefore the problem that the hydraulic oil in the fourth pilot oil path 502 cannot control the first pilot valve 61 to switch between the first working position and the second working position due to the fact that the fourth pilot oil path 502 is directly communicated with the oil tank for pressure relief is avoided.

In one embodiment, referring to fig. 3 and 4, the normal position of the first pilot valve 61 may be the first working position.

In one embodiment, referring to fig. 3 and 4, the first pilot valve 61 is self-reset by a spring of the first pilot valve 61, and the first pilot valve 61 may be a two-position four-way pilot-controlled directional control valve 62. During pumping of the pumping system, first pilot valve 61 may be maintained in a normal position, i.e., in a first operating position, by a spring.

In one embodiment, referring to fig. 3 and 4, the pumping system further includes two master cylinders 7 for alternatively pumping concrete, two signal oil paths 506, and two signal valve sets 8. Each master cylinder 7 is correspondingly provided with a signal oil path 506, a first end of each signal oil path 506 is communicated with one corresponding master cylinder 7, and second ends of the two signal oil paths 506 alternatively supply oil to the fourth pilot oil path 502. Each signal oil path 506 is provided with a signal valve group 8, and the signal valve group 8 selectively conducts the corresponding signal oil path 506. In the reversing process of the pumping system, one of the two signal valve groups 8 conducts the corresponding signal oil path 506. During the pumping process of the pumping system, each signal valve group 8 cuts off the corresponding signal oil path 506. In such a structure, the on and off of the signal valve group 8 correspond to different working processes of the pumping system, and the working process of the pumping system is detected through the signal valve group 8. Specifically, in the reversing process of the pumping system, one of the two signal valve groups 8 conducts the corresponding signal oil path 506, and the hydraulic oil of the corresponding main cylinder 7 flows to the fourth pilot oil path 502 through the corresponding signal oil path 506 and flows to the first control oil port 615 of the first pilot valve 61 through the fourth pilot oil path 502, so that the first pilot valve 61 is driven to change from the first working position to the second working position. In the pumping process of the pumping system, each signal valve group 8 cuts off the corresponding signal oil path 506, and the first pilot valve 61 is in a normal position, that is, the first pilot valve 61 is in the first working position.

How to realize the alternate pumping of the two main oil cylinders 7 is a conventional technical means in the field, and the description is omitted.

In an embodiment, referring to fig. 4, the pumping system includes a first shuttle valve 507, a second end of one of the two signal oil paths 506 is communicated with one oil inlet of the first shuttle valve 507, a second end of the other of the two signal oil paths 506 is communicated with the other oil inlet of the first shuttle valve 507, and an oil outlet of the first shuttle valve 507 is communicated with a second end of the fourth pilot oil path 502. In this configuration, the second ends of both signal oil passages 506 are alternatively supplied to fourth pilot oil passage 502 by the shuttle valve.

It will be appreciated that there are various alternative ways of supplying oil, and that in addition to the first shuttle valve 507, a combination of two check valves 85 may be used to provide an alternative supply function for the shuttle valve.

In an embodiment, referring to fig. 5, each master cylinder 7 is formed with a first collecting oil port 71 and a second collecting oil port 72, the first collecting oil port 71 and the second collecting oil port 72 are arranged at intervals along the axial direction of the corresponding master cylinder 7, the first collecting oil port 71 is located on the side of the second collecting oil port 72 extending toward the piston rod of the master cylinder 7, and the first end of the signal oil path 506 is communicated with the first collecting oil port 71 of the corresponding master cylinder 7. The signal valve group 8 includes a cartridge valve 81, a first control oil passage 82, a connecting oil passage 83, and a third throttle valve 84. The cartridge valve 81 is provided in the signal oil passage 506. A first end of the first control oil path 82 is communicated with the control port of the cartridge valve 81, and a second end of the first control oil path 82 is communicated with the second collecting port 72 of the corresponding master cylinder 7. A first end of the connection oil passage 83 communicates with the first control oil passage 82, and a signal oil passage 506 between the oil inlet of the cartridge valve 81 and the corresponding first pick-up oil port 71 communicates with a second end of the connection oil passage 83. The third throttle valve 84 is provided on the connection oil passage 83. In the reversing process of the pumping system, a piston of one of the two master cylinders 7 is located between the corresponding first collecting port 71 and the second collecting port 72, the piston moves in a direction departing from the corresponding first collecting port 71, and the corresponding cartridge valve 81 is opened to conduct the corresponding signal oil path 506. In the pumping process of the pumping system, the first collecting port 71 and the second collecting port 72 of one of the two master cylinders 7 are both located at one side of the corresponding piston, or the piston of one of the two master cylinders 7 is located between the corresponding first collecting port 71 and the corresponding second collecting port 72 and moves towards the direction of the corresponding first collecting port, the first collecting port 71 and the second collecting port 72 of the other of the two master cylinders 7 are both located at one side of the corresponding piston, or the piston of the other of the two master cylinders 7 is located between the corresponding first collecting port 71 and the corresponding second collecting port 72 and moves towards the direction of the corresponding first collecting port, and each cartridge valve 81 is closed to stop the corresponding signal oil path 506. The structure is such that, during the reversing process of the pumping system, the oil inlet chamber of one of the two master cylinders 7 is communicated with the first collecting port 71, and the oil outlet chamber of one of the two master cylinders 7 is communicated with the second collecting port 72, whereas under normal conditions, the pressure of the oil inlet chamber is greater than that of the oil return chamber, so that the valve core of the cartridge valve 81 can overcome the pressure of the control port of the cartridge valve 81 to open the cartridge valve 81, and the oil inlet and the oil outlet of the cartridge valve 81 are communicated. In the reversing process of the pumping system, the third throttle valve 84 is used for enabling the oil inlet cavity and the oil return cavity of the corresponding main oil cylinder 7 to be communicated through the corresponding signal oil path 506, the corresponding communication oil path and the corresponding first control oil path 82 on one hand, reducing the pressure difference between the oil inlet cavity and the oil return cavity to a certain extent, and slowing down the moving speed of the piston of the corresponding main oil cylinder 7 so as to enable the piston of the corresponding main oil cylinder 7 to form buffering; on the other hand, a pressure difference is formed between two ends of the third throttle valve 84 so as to open the corresponding cartridge valve 81, and therefore, the problem that the corresponding cartridge valve 81 cannot be opened due to the fact that the connection channel directly connects the signal oil path 506 between the oil inlet of the corresponding cartridge valve 81 and the corresponding first collecting oil port 71 and the corresponding first control oil path 82 without providing a throttle valve, and the pressure of the oil inlet of the corresponding cartridge valve 81 is equal to the pressure of the control oil port of the corresponding cartridge valve 81 is avoided. In the pumping process of the pumping system, when the first collecting oil port 71 and the second collecting oil port 72 of any one master cylinder 7 of the two master cylinders 7 are both located at one side of the corresponding piston, the first collecting oil port 71 and the second collecting oil port 72 are both communicated with the oil inlet cavity of the corresponding master cylinder 7, the pressure of the oil inlet of the cartridge valve 81 is relatively close to the pressure of the control oil port of the cartridge valve 81, the pressure of the oil inlet of the cartridge valve 81 is not enough to enable the valve core of the cartridge valve 81 to overcome the pressure of the control oil port of the cartridge valve 81 to open the cartridge valve 81, and the cartridge valve 81 is in a closed state. In the pumping process of the pumping system, when a piston of any one master cylinder 7 of the two master cylinders 7 is located between the corresponding first collecting oil port 71 and the corresponding second collecting oil port 72 and moves towards the direction of the corresponding first collecting port, the first collecting oil port 71 is communicated with the oil return cavity of the corresponding master cylinder 7, the second collecting oil port 72 is communicated with the oil inlet cavity of the corresponding master cylinder 7, and the pressure of the oil inlet cavity of the master cylinder 7 is usually greater than the pressure of the oil return cavity, which means that the pressure of the control oil port of the corresponding cartridge valve 81 is greater than the pressure of the oil inlet of the corresponding cartridge valve 81, and the corresponding cartridge valve 81 is in a closed state and cannot be opened.

It can be understood that, for any one master cylinder 7 of the two master cylinders 7, when the corresponding piston rod moves towards the retraction direction of the corresponding piston rod, the corresponding rod cavity is an oil inlet cavity, and the corresponding rodless cavity is an oil return cavity; when the corresponding piston rod moves towards the extending direction of the corresponding piston rod, the corresponding rodless cavity is an oil inlet cavity, and the corresponding rod cavity is an oil return cavity.

In an embodiment, referring to fig. 5, the signal valve assembly 8 further includes a check valve 85, the check valve 85 is disposed on the signal oil path 506 between the oil inlet of the cartridge valve 81 and the corresponding first oil collecting port 71, the cartridge valve 81 is disposed on the signal oil path 506 at the oil outlet side of the check valve 85, and the signal oil path 506 between the oil inlet of the cartridge valve 81 and the oil outlet of the check valve 85 is communicated with the second end of the connecting oil path 83. In the structure, in the pumping process of the pumping system, for any one of the two master cylinders 7, when the corresponding piston is located between the corresponding first collecting oil port 71 and the second collecting oil port 72 and moves towards the corresponding first collecting oil port 71, the check valve 85 stops the corresponding oil inlet cavity and the corresponding oil return cavity, namely, the corresponding rodless cavity and the corresponding rod cavity are stopped, so that the problem of pressure difference reduction of the corresponding oil inlet cavity and the corresponding oil return cavity caused by communication of the corresponding oil inlet cavity and the corresponding oil return cavity is avoided.

In an embodiment, referring to fig. 5, the signal valve assembly 8 further includes a fourth throttle valve 86 and a fifth throttle valve 87, and the fourth throttle valve 86 and the fifth throttle valve 87 are serially disposed on the signal oil path 506 between the oil inlet of the check valve 85 and the corresponding first oil collecting port 71. With this configuration, the hydraulic shock of the hydraulic oil in the signal oil passage 506 on the cartridge valve 81 can be reduced to some extent.

In an embodiment, referring to fig. 5, the pumping system further includes a second pressure relief oil path 508 and a sixth throttle 509 disposed on the second pressure relief oil path 508, each signal oil path 506 is correspondingly disposed with the second pressure relief oil path 508, and the second pressure relief oil path 508 is communicated with the signal oil path 506 on the oil outlet side of the corresponding cartridge valve 81. In general, the pressure of the hydraulic oil in the oil inlet chamber of the master cylinder 7 is relatively high, and in such a structure, the second pressure relief oil path 508 can relieve the pressure of the hydraulic oil flowing out from the oil inlet chamber of the master cylinder 7 to the oil outlet of the cartridge valve 81. The sixth throttle 509 can form a certain back pressure to avoid the problem that the signal oil path 506 on the side of the oil outlet of the cartridge valve 81 is directly communicated with the oil tank, so that the signal oil path 506 cannot work normally.

In one embodiment, as shown in fig. 3, the pumping system further comprises a second shuttle valve 510, a second oil inlet path 511, a third oil inlet path 512, and a tilt cylinder 513. The second end of the first oil-in path 500 communicates with the oil outlet of the second shuttle valve 510. A first end of the second oil-in oil path 511 communicates with one of the oil inlets of the second shuttle valve 510. A first end of the third oil inlet path 512 communicates with another oil inlet of the second shuttle valve 510. A second end of the second oil inlet passage 511 communicates with one of the rodless chambers of the tilt cylinder 513, and a second end of the third oil inlet passage communicates with the other rodless chamber of the tilt cylinder 513. During the reversing of the pumping system, the tilt cylinder 513 is reversed, and one of the two rodless chambers of the tilt cylinder 513 is communicated with the anti-cutoff cylinder 4, so that the piston rod of the anti-cutoff cylinder 4 is extended. According to the structure, in the reversing process of the pumping system, the extending action of the piston rod of the anti-flow-breaking oil cylinder 4 is related to the reversing of the tilt cylinder 513, and in the reversing process of the tilt cylinder 513, the piston rod of the anti-flow-breaking oil cylinder 4 extends out to drive the pushing piston 3 to move towards the bypass opening 14 so as to supplement the concrete in the inner cavity 21 to the material cavity 11.

In one embodiment, the reversing process of the pumping system includes a reversing process of the tilt cylinder 513, when the tilt cylinder 513 is reversed and not completely reversed, the tilt cylinder 513 drives the S-shaped pipe 200 to be detached from one concrete cylinder 100 of the two concrete cylinders 100 and move towards the other concrete cylinder 100, but not completely butted with the other concrete cylinder 100 of the two concrete cylinders 100, and during the brief reversing process of the tilt cylinder 513, since the S-shaped pipe 200 is not completely butted with any concrete pipe, concrete in the concrete cylinders 100 cannot be completely pumped into the conveying pipe 1 through the S-shaped pipe 200, and the pressure of concrete in the conveying pipe 1 is reduced to a certain extent. The extending action of the piston rod of the anti-flow-cutoff oil cylinder 4 is related to the reversing of the swinging cylinder 513, in the reversing process of the swinging cylinder 513, the piston rod of the anti-flow-cutoff oil cylinder 4 extends out to drive the pushing piston 3 to move towards the bypass opening 14 so as to supplement the concrete in the inner cavity 21 to the material cavity 11, and the pressure reduction of the concrete in the conveying pipe 1 caused by incomplete reversing of the swinging cylinder 513 and incomplete butt joint of the S pipe 200 and the concrete cylinder 100 for pumping the concrete can be compensated in the reversing process of the swinging cylinder 513.

In one embodiment, as shown in fig. 3, the pumping system further comprises a main valve block 9.

In an embodiment, as shown in fig. 3, the two signal oil paths 506 control the direction of the tilt cylinder 513 through the main valve block 9, and the specific structure of the main valve block 9 and the two signal oil paths 506 control the direction of the tilt cylinder 513 through the main valve block 9 are conventional technical means in the art, and are not described again.

In one embodiment, as shown in fig. 3, the pumping system further includes a first oil supply path P1 and a first oil return path T1. The first oil supply passage P1 selectively communicates with one of the two master cylinders 7 through the main valve group 9 so that the first oil supply passage P1 can supply oil to one of the two master cylinders 7 through the main valve group 9. The first oil return passage T1 is selectively communicated with the other of the two master cylinders 7 through the master valve group 9, so that the other of the two master cylinders 7 can be returned through the master valve group 9. The specific structure of the main valve assembly 9 is conventional in the art, and is not described in detail herein.

In one embodiment, as shown in fig. 3, the pumping system further includes a second oil supply path P2 and a second oil return path T2, the second oil supply path P2 selectively communicates with one of the two rodless chambers of the tilt cylinder 513 through the main valve block 9, so that the second oil supply path P2 can supply oil to the rodless chamber of the tilt cylinder 513 through the main valve block 9. The second oil return T2 selectively communicates with the other of the two rodless chambers of the tilt cylinder 513 via the main valve block 9 to enable oil return from the other of the two rodless chambers of the tilt cylinder 513 via the main valve block 9. The specific structure of the main valve assembly 9 is conventional in the art, and is not described in detail herein.

In one embodiment, as shown in fig. 3, the pumping system further includes a second working oil path 514 and a third working oil path 515, a first end of the second working oil path 514 is communicated with one of the two rodless chambers of the tilt cylinder 513, and a first end of the third working oil path 515 is communicated with the other of the two rodless chambers of the tilt cylinder 513. When one of the two signal oil passages 506 of the two main valve groups 9 is opened, the second oil supply passage P2 is switched between the second hydraulic oil passage 514 and the third hydraulic oil passage 515 via the main valve group 9, and the second oil return passage T2 is switched between the second hydraulic oil passage 514 and the third hydraulic oil passage 515 via the main valve group 9, so that the tilt cylinder 513 is reversed. Specifically, the main valve group 9 takes a signal from the signal oil passage 506, when one of the two signal passages is open, the second oil supply passage P2 is switched from communicating with the second working oil passage 514 to communicating with the third working oil passage 515 through the main valve group 9, and the second oil return passage T2 is switched from communicating with the third working oil passage 515 to communicating with the second working oil passage 514 through the main valve group 9; alternatively, when one of the two signal paths is opened, the second oil supply path P2 is switched from communicating with the third hydraulic oil path 515 to communicating with the second hydraulic oil path 514 by the main valve group 9, and the second oil return path T2 is switched from communicating with the second hydraulic oil path 514 to communicating with the third hydraulic oil path 515 by the main valve group 9.

The various embodiments/implementations provided herein may be combined with each other without contradiction.

The above description is only a preferred embodiment of the present application and is not intended to limit the present application, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, improvement and the like made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims (13)

1. A pumping system, comprising:

the conveying pipe is used for conveying concrete, a material cavity, a feeding hole, a discharging hole and a bypass port are formed, the feeding hole, the discharging hole and the bypass port are all communicated with the material cavity, and the bypass port is located between the feeding hole and the discharging hole;

the end part of the auxiliary pipe is covered around the bypass port, an inner cavity is formed in the auxiliary pipe, and the inner cavity is communicated with the material cavity through the bypass port;

the pushing piston is arranged in the inner cavity in a sealing and sliding mode; and

the anti-blocking oil cylinder is arranged on one side, away from the bypass port, of the pushing piston, and a piston rod of the anti-blocking oil cylinder is connected with the pushing piston;

in the reversing process of the pumping system, a piston rod of the anti-blocking oil cylinder drives the pushing piston to move towards the bypass port so as to supplement concrete in the inner cavity into the material cavity.

2. The pumping system of claim 1, further comprising a first oil inlet line, a first working oil line, and an anti-block valve set, a first end of the first working oil line being in communication with the anti-block cylinder, the anti-block valve set selectively communicating the first oil inlet line with the first working oil line or, alternatively, returning the first working oil line;

in the reversing process of the pumping system, the anti-blocking valve group is communicated with the first oil inlet oil way and the first working oil way so as to enable a piston rod of the anti-blocking oil cylinder to extend out; during the pumping process of the pumping system, the anti-blocking valve group returns oil to the first working oil path so as to retract a piston rod of the anti-blocking oil cylinder.

3. The pumping system of claim 2, wherein the anti-block valve set comprises a first pilot valve, a pilot operated directional control valve, a first pilot oil passage, a second pilot oil passage, and a third pilot oil passage, the pumping system further comprising a fourth pilot oil passage;

the hydraulic control reversing valve comprises a second oil inlet, a second oil return port, a third working oil port, a second control oil port and a third control oil port;

the first pilot valve comprises a first oil inlet, a first oil return port, a first working oil port, a second working oil port and a first control oil port, the second end of the first working oil way is communicated with the third working oil port, the first end of the first pilot oil way is communicated with the first oil inlet oil way, the second end of the first pilot oil way is communicated with the first oil inlet, the first end of the second pilot oil way is communicated with the first working oil port, the first end of the third pilot oil way is communicated with the second working oil port, and the first end of the fourth pilot oil way is communicated with the first control oil port;

the first pilot valve comprises a first working position and a second working position, when the first pilot valve is located at the first working position, the first oil inlet is communicated with the first working oil port, and the second working oil port is communicated with the first oil return port; when the first pilot valve is located at a second working position, the first oil inlet is communicated with the second working oil port, and the first working oil port is communicated with the first oil return port;

the first end of the first oil inlet oil path is communicated with the second oil inlet, the second end of the second pilot oil path is communicated with the second control oil port, and the second end of the third pilot oil path is communicated with the third control oil port;

the hydraulic control reversing valve comprises a third working position and a fourth working position, when the hydraulic control reversing valve is located at the third working position, the second oil inlet is stopped, and the third working oil port is communicated with the second oil return port; when the hydraulic control reversing valve is located at a fourth working position, the second oil inlet is communicated with the third working oil port, and the second oil return port is closed;

in the reversing process of the pumping system, the first pilot valve is in the second working position, and the hydraulic control reversing valve is in the fourth working position; in the pumping process of the pumping system, the first pilot valve is in a first working position, and the hydraulic control reversing valve is in a third working position.

4. The pumping system of claim 3, further comprising a first choke disposed on the fourth pilot oil passage.

5. The pumping system according to claim 4, further comprising a first pressure relief oil path and a second throttle valve provided on the first pressure relief oil path, wherein one end of the first pressure relief oil path is communicated with a fourth pilot oil path on a side of the first throttle valve away from the first control port.

6. A pumping system according to any of claims 3-5, further comprising:

two main oil cylinders for alternately pumping concrete;

each main oil cylinder is correspondingly provided with one signal oil way, the first end of each signal oil way is communicated with the corresponding main oil cylinder, and the second ends of the two signal oil ways are alternatively used for supplying oil to the fourth pilot oil way; and

each signal oil way is provided with one signal valve group, and the signal valve groups selectively conduct the corresponding signal oil ways;

in the reversing process of the pumping system, one of the two signal valve groups conducts the corresponding signal oil way; in the pumping process of the pumping system, each signal valve group cuts off the corresponding signal oil path.

7. The pumping system of claim 6, comprising a first shuttle valve, wherein a second end of one of the two signal oil paths is in communication with one of the oil inlets of the first shuttle valve, wherein a second end of the other of the two signal oil paths is in communication with the other of the oil inlets of the first shuttle valve, and wherein the oil outlet of the first shuttle valve is in communication with a second end of the fourth pilot oil path.

8. The pumping system of claim 6, wherein each master cylinder is formed with a first collecting oil port and a second collecting oil port, the first collecting oil port and the second collecting oil port are arranged at intervals along an axial direction of the corresponding master cylinder, the first collecting oil port is located at a side of the second collecting oil port extending toward a piston rod of the master cylinder, and a first end of the signal oil path is communicated with the first collecting oil port of the corresponding master cylinder;

the signal valve group includes:

the cartridge valve is arranged on the signal oil path;

a first end of the first control oil way is communicated with a control oil port of the cartridge valve, and a second end of the first control oil way is communicated with a second collecting oil port of the corresponding main oil cylinder;

a first end of the connecting oil way is communicated with the first control oil way, and a signal oil way between the oil inlet of the cartridge valve and the corresponding first collecting oil port is communicated with a second end of the connecting oil way; and

the third throttle valve is arranged on the connecting oil path;

in the reversing process of the pumping system, a piston of one of the two main oil cylinders is positioned between the corresponding first collecting oil port and the second collecting oil port and moves along the direction departing from the corresponding first collecting oil port, and the corresponding cartridge valve is opened to conduct the corresponding signal oil way; in the pumping process of the pumping system, a first collecting oil port and a second collecting oil port of one of the two master oil cylinders are located on one side of the corresponding piston, or a piston of one of the two master oil cylinders is located between the corresponding first collecting oil port and the corresponding second collecting oil port and moves towards the direction of the corresponding first collecting port, a first collecting oil port and a second collecting oil port of the other of the two master oil cylinders are located on one side of the corresponding piston, or a piston of the other of the two master oil cylinders is located between the corresponding first collecting oil port and the corresponding second collecting oil port and moves towards the direction of the corresponding first collecting port, and each cartridge valve is closed to stop the corresponding signal oil path.

9. The pumping system of claim 8, wherein the signal valve set further comprises a check valve, the check valve is disposed on a signal oil path between an oil inlet of the cartridge valve and the corresponding first collecting oil port, the cartridge valve is disposed on a signal oil path on one side of an oil outlet of the check valve, and a signal oil path between the oil inlet of the cartridge valve and the oil outlet of the check valve is communicated with the second end of the connecting oil path.

10. The pumping system of claim 9, wherein the signal valve block further comprises a fourth choke and a fifth choke disposed on the signal oil path between the oil inlet of the check valve and the corresponding first pickup port.

11. The pumping system according to claim 8, further comprising a second pressure relief oil path and a sixth throttle valve disposed on the second pressure relief oil path, wherein each signal oil path is correspondingly provided with the second pressure relief oil path, and the second pressure relief oil path is communicated with the signal oil path on the side of the oil outlet of the corresponding cartridge valve.

12. The pumping system of any of claims 2-5, further comprising:

the second end of the first oil inlet channel is communicated with an oil outlet of the second shuttle valve;

a first end of the second oil inlet path is communicated with one oil inlet of the second shuttle valve;

a first end of the second oil inlet path is communicated with one oil inlet of the second shuttle valve; and

the second end of the second oil inlet channel is communicated with one rodless cavity of the tilt cylinder, and the second end of the third oil inlet channel is communicated with the other rodless cavity of the tilt cylinder;

during the reversing process of the pumping system, the tilt cylinder is reversed, and one of the two rodless cavities of the tilt cylinder is communicated with the anti-flow-cutoff oil cylinder, so that a piston rod of the anti-flow-cutoff oil cylinder extends out.

13. A pumping machine, characterized in that it comprises a pumping system according to any one of claims 1 to 12.

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